WO2012039378A1 - Dispositif d'entraînement pour véhicule - Google Patents

Dispositif d'entraînement pour véhicule Download PDF

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Publication number
WO2012039378A1
WO2012039378A1 PCT/JP2011/071333 JP2011071333W WO2012039378A1 WO 2012039378 A1 WO2012039378 A1 WO 2012039378A1 JP 2011071333 W JP2011071333 W JP 2011071333W WO 2012039378 A1 WO2012039378 A1 WO 2012039378A1
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WO
WIPO (PCT)
Prior art keywords
oil
oil passage
electrical machine
rotating electrical
rotor
Prior art date
Application number
PCT/JP2011/071333
Other languages
English (en)
Japanese (ja)
Inventor
糟谷悟
鬼頭昌士
関祐一
▲高▼▲橋▼佑介
杉坂繁
Original Assignee
アイシン・エィ・ダブリュ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by アイシン・エィ・ダブリュ株式会社 filed Critical アイシン・エィ・ダブリュ株式会社
Priority to CN201180041612XA priority Critical patent/CN103081311A/zh
Priority to DE112011102544T priority patent/DE112011102544T5/de
Publication of WO2012039378A1 publication Critical patent/WO2012039378A1/fr

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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/40—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the assembly or relative disposition of components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L50/00—Electric propulsion with power supplied within the vehicle
    • B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
    • B60L50/15—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with additional electric power supply
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
    • B60L50/00—Electric propulsion with power supplied within the vehicle
    • B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
    • B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/12—Details not specific to one of the before-mentioned types
    • F16D25/123—Details not specific to one of the before-mentioned types in view of cooling and lubrication
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/006—Structural association of a motor or generator with the drive train of a motor vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/64—Electric machine technologies in electromobility
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/7072—Electromobility specific charging systems or methods for batteries, ultracapacitors, supercapacitors or double-layer capacitors

Definitions

  • the present invention includes an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to a wheel, a friction engagement device that selectively drives and connects the input member and the output member, an input member, and an output member. And a rotary electric machine provided on a power transmission path connecting the two.
  • Patent Document 1 a device described in Patent Document 1 below is already known as a vehicle drive device as described above.
  • reference numerals in Patent Document 1 are quoted in [].
  • Permanent magnets [41] which are supplied to an oil passage [oil passages 38a, 39d, 39b, 39c] formed in the rotor [11] of the [motor / generator MG] and are provided in the rotating electrical machine when flowing through the oil passage. ] Can be cooled.
  • the coil end portion is also configured to be cooled by oil overflowing so as to bypass the axially outer side of the friction member. Thereby, both a friction member and a rotary electric machine can be cooled.
  • the friction member of the friction engagement device is disposed in a space opened in the axial direction, and the open space and the accommodation space in which the rotating electrical machine is accommodated have a boundary. It is integrally formed without.
  • a sufficient cooling performance of the friction member is to be ensured, it is necessary to ensure a large amount of oil supplied to the friction member.
  • a large oil pump is required. As a result, the energy for driving the pump is increased and the weight of the oil pump itself is increased, which may reduce the energy efficiency.
  • a rotating electrical machine provided on a power transmission path that connects the output member
  • the vehicle drive device has a characteristic configuration that houses at least the friction member of the friction engagement device and is filled with oil.
  • a third oil passage that supplies oil discharged from the storage space to the accommodation space.
  • driving connection means a state where two rotating elements are connected so as to be able to transmit a driving force, and the two rotating elements are connected so as to rotate integrally, or the two
  • the rotating element is used as a concept including a state in which the driving force is connected to be transmitted through one or more transmission members.
  • a transmission member include various members that transmit rotation at the same speed or a variable speed, and include, for example, a shaft, a gear mechanism, a belt, a chain, and the like.
  • an engagement device that selectively transmits rotation and driving force for example, a friction clutch or a meshing clutch may be included.
  • the “rotary electric machine” is used as a concept including a motor (electric motor), a generator (generator), and a motor / generator that performs both functions of the motor and the generator as necessary.
  • At least the accommodation is achieved by filling the inside of the accommodation oil chamber with oil and supplying the oil to the accommodation oil chamber from the first oil passage and discharging it from the second oil passage.
  • the friction member can be sufficiently cooled by an amount of oil that can fill the inside of the oil chamber and the first oil passage. That is, it is possible to reduce the amount of supply oil required to sufficiently secure the cooling performance of the friction member. Therefore, it is not necessary to increase the size of the oil pump for discharging oil, and the reduction in energy efficiency can be suppressed.
  • emitted through the 2nd oil path from the accommodation oil chamber is supplied to an accommodation space via a 3rd oil path, and the rotary electric machine accommodated in the said accommodation space is cooled. can do. That is, since the rotating electrical machine can be cooled using the oil that has cooled the friction member, the amount of supply oil necessary for securing the cooling performance can be reduced from this point as well. Therefore, according to said characteristic structure, the vehicle drive device which can cool both a friction member and a rotary electric machine efficiently can be implement
  • the third oil passage extends in the axial direction from an oil supply portion that supplies oil to the coil end portion of the stator from above the stator of the rotating electrical machine and a connection portion between the second oil passage. It is preferable to have an oil passage and a radial oil passage extending in the radial direction so as to communicate the axial oil passage and the oil supply section.
  • the oil flowing through the axial oil passage connected to the second oil passage through the connection portion and the radial oil passage communicating with the axial oil passage is supplied to the oil supply portion. Can be supplied. Thereafter, oil can be supplied to the coil end portion of the stator of the rotating electrical machine via the oil supply portion, and the coil end portion can be cooled. At that time, oil is supplied to the coil end portion from above the stator via the oil supply portion, and the supplied oil flows down along the coil end portion in the vertical direction. Therefore, the whole coil end part can be cooled efficiently.
  • the oil supply unit includes a tubular member extending in the axial direction above the stator, and is directed to the coil end unit at a position overlapping the coil end unit in a radial view of the tubular member. It is preferable to provide a supply opening that opens.
  • “having overlapping portions when viewed in a predetermined direction” means that when the viewpoint is moved in each direction orthogonal to the line-of-sight direction with the predetermined direction as the line-of-sight direction, the two members This means that the viewpoints that appear to overlap each other exist in at least some areas.
  • a part of the third oil passage can be formed above the stator with a relatively simple configuration using a tubular member having a predetermined opening (supply opening). Further, since the supply opening is provided at a position of the tubular member extending along the axial direction so as to overlap with the coil end portion in the radial direction, the oil supply portion is provided to the coil end portions on both sides in the axial direction of the stator. The oil from can be properly supplied.
  • the case that accommodates at least the rotating electrical machine and the frictional engagement device and the rotor of the rotating electrical machine are supported, and both sides in the axial direction and the radially outer side of the frictional engagement device are surrounded and housed therein.
  • the accommodation oil chamber filled with oil can be formed in the inside while supporting the rotor of the rotating electrical machine by the rotor support member. Further, the rotor support member can be rotatably supported with respect to the case via the support bearing. Moreover, in this structure, a support bearing can be lubricated using the oil which flows through the bearing supply oil path connected to a 2nd oil path via a connection part. Thereafter, oil can be supplied to the housing space via the bearing discharge oil passage, and the rotating electrical machine housed in the housing space can be cooled. Therefore, the rotating electrical machine can be cooled while lubricating the support bearing.
  • a casing having at least a support wall extending axially adjacent to the rotating electrical machine and at least radially extending, the rotor supporting the rotor of the rotating electrical machine; Oil is provided to the support member and is formed so as to open radially inward, and oil is supplied from the oil collector to the coil end portion of the stator of the rotating electrical machine disposed in the housing space.
  • a fourth oil passage wherein the third oil passage is provided on the support wall and has a third oil passage opening that opens toward the rotating electrical machine, It is preferable that the oil passage opening is provided on the radially inner side of the oil collecting portion.
  • the third oil passage is formed in the support wall adjacent to the rotating electrical machine in the axial direction, the third oil passage can be configured without requiring an additional member. Further, in this configuration, oil supplied from the third oil passage opening of the third oil passage is collected by an oil collecting portion provided in the rotor support member on the radially outer side of the third oil passage opening. can do. Thereafter, the oil collected by the oil collecting part is supplied to the coil end part of the stator of the rotating electrical machine disposed in the accommodating space via the fourth oil passage, and the coil end part is efficiently cooled. Can do.
  • the sensor further includes a rotation sensor having a sensor stator fixed to the support wall, and a sensor rotor disposed on a radially outer side of the sensor stator and fixed to a side surface of the rotor support member on the support wall side,
  • the third oil passage opening is provided on a contact surface of the support wall with the sensor stator, and the third oil passage opening overlaps the third oil passage opening in the axial direction of the sensor stator. It is preferable that an axial through-hole that penetrates the sensor stator in the axial direction is provided.
  • the third oil passage opening is formed at the radial position of the sensor stator, the radial distance between the third oil passage opening and the oil collecting portion is relatively short, It becomes easy to guide the oil from the third oil passage opening to the oil collecting part. Further, since the third oil passage formed in the support wall is formed to extend to the contact surface of the support wall with the sensor stator, the third oil passage opening, the rotor support member, and the rotor support member The distance in the axial direction between the oil collecting portion and the oil collecting portion provided in the oil collecting portion is also reduced, and from this point, the oil from the third oil passage opening can be easily guided to the oil collecting portion.
  • the sensor stator is provided with an axial through hole penetrating the sensor stator in the axial direction at a position overlapping the third oil passage opening in the axial direction.
  • the oil from the third oil passage opening can be appropriately guided to the oil collecting part. Therefore, the oil supplied from the third oil passage can be appropriately guided to the accommodation space via the oil collecting portion and the fourth oil passage, and the coil end portion can be efficiently cooled.
  • the oil collecting portion is formed between the sensor rotor and the rotor support member.
  • the oil collecting portion can be formed between the sensor rotor and the rotor support member by using the sensor rotor of the rotation sensor.
  • a vehicle drive device including a rotating electrical machine as a vehicle driving force source is provided with the above rotation sensor for the purpose of accurately detecting the rotational position of the rotor with respect to the stator of the rotating electrical machine. Therefore, an oil collecting part can be formed without requiring an additional member, and an increase in cost can be suppressed.
  • FIG. 1 It is a schematic diagram which shows schematic structure of the drive device which concerns on 1st embodiment. It is a fragmentary sectional view of a drive device. It is the elements on larger scale in FIG. It is the elements on larger scale in FIG. It is a graph which shows the cooling effect of the clutch by this invention. It is a fragmentary sectional view of the drive device concerning a second embodiment.
  • FIG. 1 is a schematic diagram illustrating a schematic configuration of a driving device D according to the present embodiment.
  • the driving device D is a driving device (hybrid driving device) for a hybrid vehicle that uses one or both of the internal combustion engine E and the rotating electrical machine MG as a driving force source for the wheels W of the vehicle.
  • the drive device D is configured as a drive device for a so-called 1-motor parallel type hybrid vehicle.
  • the drive device D according to the present embodiment will be described in detail.
  • the drive device D includes an input shaft I that is drivingly connected to the internal combustion engine E, an output shaft O that is drivingly connected to the wheels W, a rotating electrical machine MG, and a speed change mechanism. TM and an intermediate shaft M that is drivingly connected to the rotating electrical machine MG and that is drivingly connected to the speed change mechanism TM.
  • the drive device D includes a clutch CL that selectively drives and connects the input shaft I and the output shaft O, a counter gear mechanism C, and an output differential gear device DF.
  • the rotating electrical machine MG is provided on a power transmission path connecting the input shaft I and the output shaft O.
  • the rotating shaft MG includes the intermediate shaft M, the speed change mechanism TM, the counter gear mechanism C, and the output differential gear device DF. Via the output shaft O.
  • Each of these components is housed in a case (drive device case) 1.
  • the input shaft I corresponds to the “input member” in the present invention
  • the output shaft O corresponds to the “output member” in the present invention.
  • the “axial direction” and “diameter” are based on the input shaft I, the intermediate shaft M, and the rotational axis of the rotating electrical machine MG arranged on the same axis.
  • Each direction of “direction” and “circumferential direction” is defined.
  • the internal combustion engine E side (the right side in FIG. 2) with respect to the rotating electrical machine MG is defined as the first axial direction A1 side, and the opposite side of the rotating electrical machine MG from the internal combustion engine E (FIG. 2). Is defined as the second axial direction A2 side.
  • driving force is used synonymously with torque.
  • the internal combustion engine E is a device that is driven by combustion of fuel inside the engine to extract power.
  • a gasoline engine, a diesel engine, or the like can be used as the internal combustion engine E.
  • An output rotation shaft such as a crankshaft of the internal combustion engine E is drivingly connected to the input shaft I.
  • the input shaft I is drivingly connected to the rotating electrical machine MG and the intermediate shaft M via the clutch CL, and the input shaft I is selectively connected to the rotating electrical machine MG and the intermediate shaft M by the clutch CL.
  • the internal combustion engine E and the rotary electric machine MG are drivingly connected via the input shaft I, and in the released state of the clutch CL, the internal combustion engine E and the rotary electric machine MG are separated.
  • the rotating electrical machine MG includes a stator St and a rotor Ro, and functions as a motor (electric motor) that generates power by receiving power supply, and a generator (power generation) that generates power by receiving power supply. Function). Therefore, rotating electrical machine MG is electrically connected to a power storage device (not shown). A battery, a capacitor, or the like can be used as the power storage device.
  • the rotating electrical machine MG is powered by receiving electric power from the battery, or supplies electric power generated by the torque of the internal combustion engine E or the inertial force of the vehicle to the battery for storage.
  • the rotor Ro of the rotating electrical machine MG is drivingly connected so as to rotate integrally with the intermediate shaft M.
  • the intermediate shaft M is an input shaft (transmission input shaft) of the speed change mechanism TM.
  • the speed change mechanism TM is a mechanism that changes the rotational speed of the intermediate shaft M at a predetermined speed ratio and transmits it to the speed change output gear G.
  • an automatic stepped transmission mechanism that is capable of switching between a plurality of shift stages having different gear ratios is used as such a transmission mechanism TM.
  • an automatic continuously variable speed change mechanism that can change the speed ratio steplessly, a manual stepped speed change mechanism that is capable of switching a plurality of speed stages having different speed ratios, or the like may be used.
  • the speed change mechanism TM transmits the rotation and torque input to the intermediate shaft M to the speed change output gear G while changing the speed and converting the torque according to a predetermined speed change ratio at each time point.
  • the transmission output gear G is drivingly connected to an output differential gear device DF via a counter gear mechanism C.
  • the output differential gear unit DF is drivingly connected to the wheel W via the output shaft O.
  • the output differential gear device DF distributes and transmits the rotation and torque input to the output differential gear device DF to the two left and right wheels W.
  • the drive device D can cause the vehicle to travel by transmitting the torque of one or both of the internal combustion engine E and the rotating electrical machine MG to the wheels W.
  • the input shaft I and the intermediate shaft M are arranged coaxially, and the output shaft O is arranged parallel to each other on an axis different from the input shaft I and the intermediate shaft M.
  • a multi-axis configuration is adopted.
  • Such a configuration is suitable as a configuration of the driving device D mounted on, for example, an FF (Front-Engine-Front-Drive) vehicle.
  • the case 1 houses at least the rotating electrical machine MG and the clutch CL.
  • the case 1 includes a case peripheral wall 2 that covers the outer periphery of each housing component such as the rotating electrical machine MG and the speed change mechanism TM, a first support wall 3 that closes an opening on the axial first direction A1 side of the case peripheral wall 2, and the first A second support wall 11 disposed between the rotating electrical machine MG and the speed change mechanism TM in the axial direction on the second axial direction A2 side of the support wall 3;
  • the case 1 has an end support wall (not shown) that closes the end of the case peripheral wall 2 on the second axial direction A2 side.
  • the first support wall 3 extends in the radial direction and the circumferential direction on the axial first direction A1 side of the rotating electrical machine MG and the clutch CL.
  • the first support wall 3 is disposed adjacent to the rotating electrical machine MG and the clutch CL at a predetermined interval on the first axial direction A1 side.
  • the first support wall 3 has an axial through hole, and the input shaft I is inserted through the through hole. As a result, the input shaft I passes through the first support wall 3 and is inserted into the case 1.
  • a seal member 65 is disposed between the outer peripheral surface of the input shaft I and the inner peripheral surface of the through hole of the first support wall 3.
  • the first support wall 3 has a cylindrical protrusion 4 that protrudes in the axial direction toward the second axial direction A2.
  • the first support wall 3 rotatably supports the rotor support member 30 on the first axial direction A1 side of the rotating electrical machine MG by the cylindrical protrusion 4.
  • the second support wall 11 extends in the radial direction and the circumferential direction on the second axial direction A2 side of the rotating electrical machine MG and the clutch CL.
  • the second support wall 11 corresponds to the “support wall” in the present invention.
  • the second support wall 11 is disposed adjacent to the rotating electrical machine MG and the clutch CL at a predetermined interval on the second axial direction A2 side.
  • the case 1 has two case parts, a first case part that accommodates the rotating electrical machine MG and the clutch CL, and a second case part that accommodates the speed change mechanism TM and the like. I know.
  • the second support wall 11 includes a partition wall 12 formed to extend radially inward from the case peripheral wall 2, a pump body 13 and a pump cover 14 that form a pump chamber that houses the oil pump 19. It has.
  • a central opening 12 a is formed in the central portion of the partition wall 12 in the radial direction, and the pump body 13 is inserted through the central opening 12 a and is disposed on the radially inner side of the partition wall 12.
  • a pump cover 14 is disposed so as to contact the pump body 13 from the second axial direction A2 side.
  • the pump cover 14 extends in the radial direction and the circumferential direction, and the end portion on the outer side in the radial direction is located in the vicinity of the inner peripheral surface of the case peripheral wall 2.
  • the pump body 13 and the pump cover 14 each have an axial through hole, and the intermediate shaft M is inserted through the through hole. Thereby, the intermediate shaft M passes through the second support wall 11.
  • a cylindrical protrusion 37 of the rotor support member 30 is inserted between the pump body 13 and the intermediate shaft M that are arranged coaxially.
  • the pump body 13 has a cylindrical protrusion 15 that protrudes in the axial direction toward the first axial direction A1.
  • the second support wall 11 rotatably supports the rotor support member 30 on the second axial direction A2 side of the rotating electrical machine MG by the cylindrical protrusion 15.
  • An oil pump 19 is accommodated in a pump chamber formed between the pump body 13 and the pump cover 14.
  • the oil pump 19 is an inscribed gear pump having an inner rotor and an outer rotor.
  • the inner rotor is splined so as to rotate integrally with the cylindrical protrusion 37 of the rotor support member 30.
  • the oil pump 19 sucks oil from an oil pan (not shown) as the rotor support member 30 rotates, discharges the sucked oil, and feeds the oil to the clutch CL, the speed change mechanism TM, the rotating electrical machine MG, and the like. Supply.
  • oil passages are formed inside the pump body 13, the pump cover 14, the intermediate shaft M, and the like, and the oil discharged by the oil pump 19 is connected to the oil supply target through these oil passages. Is supplied to each part.
  • the input shaft I arranged so as to penetrate the first support wall 3 is drivably coupled to the internal combustion engine E via a damper on the first support wall 3 in the first axial direction A1 side. Yes.
  • a hole Ia extending in the axial direction is formed at the radial center of the end of the input shaft I on the second axial direction A2 side.
  • the inner peripheral surface of the hole Ia and the outer peripheral surface of the input shaft I communicate with each other via a discharge through hole Ib extending in the radial direction.
  • the input shaft I is connected to the clutch hub 26 via a flange portion formed so that the end portion on the second axial direction A2 side extends radially outward.
  • the intermediate shaft M disposed so as to penetrate the second support wall 11 is splined to the cylindrical protrusion 37 of the rotor support member 30.
  • the end of the intermediate shaft M on the first axial direction A1 side is inserted in the axial direction with respect to a hole Ia formed in the input shaft I.
  • the intermediate shaft M has a plurality of oil passages including a hydraulic oil passage 25 formed so as to communicate with the hydraulic pressure chamber H1 of the clutch CL and a second oil passage L2 described later.
  • the clutch CL is a friction engagement device that is provided so as to be able to switch between transmission and interruption of the driving force between the input shaft I and the intermediate shaft M, and selectively drive-couples the internal combustion engine E and the rotating electrical machine MG.
  • the clutch CL fulfills a function of separating the internal combustion engine E from the rotating electrical machine MG and the output shaft O, for example, in an electric travel mode (EV mode) in which the vehicle travels using only the torque of the rotating electrical machine MG. That is, the clutch CL functions as a friction engagement device for separating the internal combustion engine.
  • the clutch CL is configured as a wet multi-plate clutch mechanism. As shown in FIG. 3, the clutch CL includes a clutch hub 26, a plurality of friction plates 27, and a piston 28.
  • a rotor support member 30 formed so as to cover the periphery thereof.
  • the rotor support member 30 functions as a clutch housing that houses the clutch CL.
  • the rotor support member 30 is also configured to function as a clutch drum.
  • a plurality of friction plates 27 are provided between the rotor support member 30 splined to the intermediate shaft M and the clutch hub 26 integrally connected to the input shaft I.
  • a piston 28 as a pressing member is disposed on the second axial direction A2 side with respect to the friction plate 27.
  • a liquid-tight working hydraulic chamber H1 is formed between the rotor support member 30 and the piston 28.
  • Oil that is discharged from the oil pump 19 and adjusted to a predetermined oil pressure by the oil pressure control device VB is supplied to the working oil pressure chamber H1 via a working oil passage 25 formed inside the intermediate shaft M. Engagement and release of the clutch CL are controlled according to the hydraulic pressure supplied to the working hydraulic chamber H1.
  • a circulating hydraulic chamber H2 is formed on the opposite side of the piston 28 from the operating hydraulic chamber H1. The oil discharged from the oil pump 19 is supplied to the circulating hydraulic chamber H2 through the first oil passage L1.
  • the rotating electrical machine MG is arranged on the radially outer side of the clutch CL.
  • the rotating electrical machine MG is disposed at a position overlapping the clutch CL when viewed in the radial direction.
  • the stator St of the rotating electrical machine MG is fixed to the case 1.
  • the rotor Ro is rotatably supported via a rotor support member 30 on the radially inner side of the stator St.
  • the stator St includes a cylindrical stator core fixed to the case 1 and a coil wound around the stator core.
  • the part which protrudes in an axial direction from the both end surfaces of the axial direction of a stator core among coils is a coil end part Ce.
  • the coil end portion on the first axial direction A1 side is referred to as a first coil end portion Ce1
  • the coil end portion on the second axial direction A2 side is referred to as a second coil end portion Ce2.
  • the stator St and the rotor Ro of the rotating electrical machine MG are arranged in a state of being accommodated in the rotating electrical machine accommodating space S.
  • the rotating electrical machine housing space S is formed as an annular space formed coaxially with the input shaft I and the intermediate shaft M.
  • the cross section of the rotating electrical machine housing space S in a plane including the rotation axis of the input shaft I and the intermediate shaft M is the first support wall 3 and the second support wall 11 (here, the partition wall 12) in the axial direction. ) And the area between the radially inner end face of the rotor Ro and the case peripheral wall 2 in the radial direction.
  • the rotating electrical machine housing space S is a space that extends outward in the radial direction from the rotor support member 30 in the space inside the first case portion constituting the case 1.
  • the rotating electrical machine housing space S is formed so as to surround the periphery of the stator St and the rotor Ro along the outer edges thereof. At that time, the gaps between the stator St and the rotor Ro and the case 1 (the first support wall 3, the partition wall 12, and the case peripheral wall 2) are within a predetermined distance.
  • the outline of the range occupied by the rotating electrical machine housing space S is indicated by a broken line.
  • the rotating electrical machine housing space S corresponds to the “housing space” in the present invention.
  • the rotor support member 30 supports the rotor Ro while being rotatable with respect to the case 1.
  • the rotor support member 30 is supported by the first support wall 3 via the first bearing 61 on the first axial direction A1 side in the state where the rotor Ro is fixed to the outer peripheral portion thereof, and is second on the second axial direction A2 side. It is supported by the pump body 13 constituting the second support wall 11 via the bearing 62.
  • the rotor support member 30 is formed so as to cover the periphery of the clutch CL disposed therein.
  • the rotor support member 30 includes a first radial extending portion 31 that extends in the radial direction on the first axial direction A1 side of the clutch CL, and a second radial direction that extends in the radial direction on the second axial direction A2 side of the clutch CL.
  • the extending portion 36 and an axially extending portion 41 extending in the axial direction on the radially outer side of the clutch CL are provided.
  • the first radial extending portion 31 extends in the radial direction and the circumferential direction on the first axial direction A1 side of the clutch CL.
  • the first radially extending portion 31 has an axial through hole, and the input shaft I is inserted through the through hole.
  • the input shaft I passes through the first radially extending portion 31 and is inserted into the rotor support member 30.
  • the first radially extending portion 31 has a uniform thickness as a whole and is formed in a dish shape so that the radially inner portion is positioned slightly closer to the axial second direction A2 side than the radially outer portion. Yes.
  • the 1st radial direction extension part 31 has the cylindrical protrusion part 32 which protrudes toward the axial 1st direction A1 side in the edge part inside the radial direction.
  • the cylindrical protruding portion 32 is formed so as to surround the input shaft I.
  • a third bearing 63 is disposed between the cylindrical protrusion 32 and the input shaft I.
  • a first bearing 61 is arranged between the cylindrical protrusion 32 and the cylindrical protrusion 4 of the first support wall 3.
  • the 1st bearing 61 and the 3rd bearing 63 are arrange
  • the first bearing 61 corresponds to the “support bearing” in the present invention.
  • the second radially extending portion 36 extends in the radial direction and the circumferential direction on the second axial direction A2 side of the clutch CL.
  • the second radially extending portion 36 has an axial through hole, and the intermediate shaft M is inserted through the through hole. Accordingly, the intermediate shaft M is inserted into the rotor support member 30 through the second radially extending portion 36.
  • the second radially extending portion 36 is formed in a flat plate shape having at least a portion thereof having a uniform thickness as a whole and extending flat in the radial direction.
  • the 2nd radial direction extension part 36 has the cylindrical protrusion part 37 which protrudes toward the axial 2nd direction A2 side in the edge part inside the radial direction.
  • the cylindrical protrusion 37 is formed so as to surround the periphery of the intermediate shaft M.
  • the cylindrical projecting portion 37 is in contact with the outer peripheral surface of the intermediate shaft M at a part of the inner peripheral surface in the axial direction over the entire circumferential direction.
  • a second bearing 62 is arranged between the cylindrical protrusion 37 and the cylindrical protrusion 15 of the pump body 13.
  • the cylindrical protruding portion 37 is splined to the intermediate shaft M at the inner peripheral portion of the end portion on the second axial direction A2 side so as to rotate integrally with the intermediate shaft M.
  • the cylindrical protrusion 37 is spline-connected to the inner rotor at the outer peripheral portion of the end portion on the second axial direction A2 side so as to rotate integrally with the inner rotor of the oil pump 19. Accordingly, the cylindrical protrusion 37 functions as a pump drive shaft that rotationally drives the inner rotor.
  • a working hydraulic chamber H ⁇ b> 1 is formed between the second radially extending portion 36 and the piston 28.
  • the second radially extending portion 36 has a generally cylindrical sensor mounting portion 38 formed at the radially outer end thereof so as to protrude toward the axial second direction A2.
  • the sensor attachment portion 38 has a predetermined thickness in the axial direction and the radial direction.
  • the sensor mounting portion 38 is disposed at a position where the radially inner portion overlaps the friction plate 27 and the pressing portion of the piston 28 in the axial direction.
  • the sensor mounting portion 38 is disposed at a position overlapping the second bearing 62 and the second coil end portion Ce2 in the radial direction view.
  • the axially extending portion 41 extends radially outward of the clutch CL in the axial direction and the circumferential direction.
  • the axially extending portion 41 is formed in a cylindrical shape, and connects the first radially extending portion 31 and the second radially extending portion 36 in the axial direction.
  • the axially extending portion 41 is formed integrally with the first radially extending portion 31.
  • the axially extending portion 41 is connected to the second radially extending portion 36 by bolts. Note that these may be connected by welding or the like.
  • a rotor Ro of the rotating electrical machine MG is fixed to the outer peripheral portion of the axially extending portion 41.
  • the axially extending portion 41 is formed in a cylindrical shape and supports a rotor Ro from the radially inner side, and is formed in an annular shape from the axial second direction A2 side of the rotor Ro.
  • a second support portion 43 for supporting the.
  • the second support portion 43 extends radially outward from the end of the first support portion 42 on the second axial direction A2 side.
  • the second support portion 43 has a predetermined thickness in the axial direction and the radial direction.
  • An annular rotor holding member 44 is extrapolated from the first axial direction A1 side to the first support portion 42, and this rotor holding member 44 holds the rotor Ro from the first axial direction A1 side.
  • the rotation sensor 21 is provided between the pump body 13 constituting the second support wall 11 and the second radially extending portion 36 on the second axial direction A2 side of the rotor support member 30.
  • the rotation sensor 21 is a sensor for detecting the rotational position of the rotor Ro relative to the stator St of the rotating electrical machine MG.
  • a resolver is used in this example.
  • the rotation sensor 21 includes a sensor rotor 22 and a sensor stator 23.
  • the sensor stator 23 is fixed to the pump body 13 outside the cylindrical protrusion 15 in the radial direction.
  • the sensor rotor 22 is disposed on the outer side in the radial direction of the sensor stator 23 and is fixed to the sensor attachment portion 38 of the second radial extension portion 36 of the rotor support member 30.
  • such a rotation sensor 21 is arranged on the radially outer side of the second bearing 62 at a position overlapping the second bearing 62 in the radial direction. Moreover, the rotation sensor 21 is arrange
  • the clutch CL is cooled using a cooling structure mainly composed of the first oil passage L ⁇ b> 1, the second oil passage L ⁇ b> 2, and the rotor support member 30.
  • the oil supplied to the circulating hydraulic chamber H2 through the first oil passage L1 is configured to cool the plurality of friction plates 27 disposed in the circulating hydraulic chamber H2.
  • the oil after cooling the friction plate 27 is discharged from the circulating hydraulic chamber H2 through the second oil passage L2.
  • the circulating hydraulic chamber H2 corresponds to the “accommodating oil chamber” in the present invention.
  • the space that occupies most of the space excluding the working hydraulic chamber H1 is the circulating hydraulic pressure in which the plurality of friction plates 27 are arranged. It becomes chamber H2.
  • an axial oil passage L ⁇ b> 1 a that extends linearly along the axial direction is formed in the cylindrical protrusion 37 of the rotor support member 30.
  • the axial oil passage L1a constitutes a part of the first oil passage L1, the end portion on the axial first direction A1 side communicates with the circulating hydraulic chamber H2, and the axial oil passage L1 side on the second axial direction A2 side.
  • the end portion communicates with the hydraulic control device VB via an oil passage formed in the case 1. Then, the oil discharged by the oil pump 19 and adjusted to a predetermined hydraulic pressure by the hydraulic pressure control device VB is supplied to the circulation hydraulic chamber H2 via the first oil passage L1 including the axial oil passage L1a.
  • an oil cooler 91 is inserted in the first oil passage L1 extending from the hydraulic control device VB. The oil from the first oil passage L1 is cooled by the oil cooler 91 and then supplied to the circulation hydraulic chamber H2.
  • the third bearing 63 is a bearing with a sealing function (here, a needle bearing with a seal ring) configured to ensure a certain degree of liquid tightness. Further, a part of the inner peripheral surface in the axial direction of the cylindrical protrusion 37 is in contact with the outer peripheral surface of the intermediate shaft M over the entire circumferential direction. Therefore, the circulating hydraulic chamber H2 is in a liquid-tight state, and the oil is supplied, whereby the circulating hydraulic chamber H2 is basically filled with oil having a predetermined pressure or higher. Thereby, in the drive device D according to the present embodiment, it is possible to efficiently cool the plurality of friction plates 27 with a large amount of oil filled in the circulating hydraulic chamber H2.
  • FIG. 5 shows an experimental result of an experiment conducted for confirming the cooling effect of the clutch CL in the hybrid drive device H according to the present embodiment.
  • the temperature change of the friction plate 27 was measured when the oil pump 19 was driven at a constant rotational speed while controlling the operation of the clutch CL so that the plurality of friction plates 27 slide on each other.
  • “Example” is the measurement data obtained by the hybrid drive apparatus H according to this embodiment.
  • “Comparative Example” indicates that the inside of the rotor support member 30 that houses the clutch CL is not in an oil-tight state (in this example, the first radially extending portion 31 is removed). Measurement data with the drive device of the configuration. In addition, it was set as the same conditions except the conditions regarding the presence or absence of the 1st radial direction extension part 31 between these Examples and a comparative example.
  • the temperature of the friction plate rises within a relatively short time. This is presumably because the oil supplied to the friction plate immediately flows radially outward and passes through the friction plate, and the entire friction plate cannot be cooled sufficiently.
  • the hybrid drive device H of the example it can be seen that the increase in the temperature of the friction plate 27 is suppressed within a predetermined range even after a certain amount of time has elapsed. This is because the circulating hydraulic chamber H2 is filled with oil discharged from the oil pump 19 and supplied via the hydraulic control device VB and the first oil passage L1, and the entire friction plate 27 is separated from the oil in the circulating hydraulic chamber H2. It is considered that the friction plate 27 can be efficiently cooled by the contact.
  • the driving device of the comparative example in order to sufficiently secure the cooling performance of the friction plate, it is necessary to secure a large amount of oil supplied per unit time to the friction plate.
  • the energy for driving the pump is increased and the weight of the oil pump itself is increased, which may reduce the energy efficiency.
  • the amount of supply oil required to sufficiently secure the cooling performance of the friction plate 27 may be relatively small. Therefore, it is not necessary to increase the size of the oil pump 19, and it is possible to suppress a decrease in energy efficiency.
  • the oil that has cooled the plurality of friction plates 27 flows radially inward along the first radially extending portion 31, and the clutch hub 26 and the first radially extending portion 31 It passes through the fourth bearing 64 disposed therebetween and is discharged from the circulating hydraulic chamber H2.
  • the fourth bearing 64 is formed with an axial groove and a radial groove for circulating oil.
  • the oil that has passed through the fourth bearing 64 is guided from the circulating hydraulic chamber H2 to the inside of the intermediate shaft M through the discharge oil passage L2a.
  • the drain oil passage L2a is an oil passage (gap oil passage) formed in a gap between the clutch hub 26 and the first radially extending portion 31 on the radially inner side of the fourth bearing 64.
  • the oil is guided through these portions to an axial oil passage L2b formed inside the intermediate shaft M.
  • the axial oil passage L2b is formed to extend linearly along the axial direction.
  • a radial oil passage L2c extending linearly along the radial direction is also formed inside the intermediate shaft M.
  • the axial oil passage L2b communicates with the discharge oil passage L2a at the end portion on the axial first direction A1 side, and communicates with the radial oil passage L2c at the end portion on the second axial direction A2 side.
  • the radial oil passage L ⁇ b> 2 c opens on the outer peripheral surface of the intermediate shaft M. This opening is a connecting portion with a third oil passage L3 (here, an axial oil passage L3a) described below.
  • the second oil passage L2 is configured by the discharge oil passage L2a, the axial oil passage L2b, and the radial oil passage L2c. These oil passages constituting the second oil passage L2 are connected in series in the order described.
  • the rotating electrical machine MG uses a cooling structure mainly composed of a third oil passage L3 formed above the intermediate shaft M (upward in the vertical direction). And cooled.
  • the oil discharged from the circulating hydraulic chamber H2 through the second oil passage L2 is supplied to the rotating electrical machine accommodation space S through the third oil passage L3, and is disposed in the rotating electrical machine accommodation space S.
  • the rotating electric machine MG is configured to be cooled.
  • the pump cover 14 has a cylindrical protruding portion 16 that protrudes from the radially inner end portion toward the second axial direction A2.
  • the cylindrical protrusion 16 is formed so as to surround the periphery of the intermediate shaft M. As shown in FIG. 3, the cylindrical protrusion 16 overlaps with the radial oil passage L ⁇ b> 2 c when viewed in the radial direction, and extends in the radial direction to communicate with the inner peripheral opening formed on the inner peripheral surface thereof.
  • a communication hole 71 is formed.
  • an axial oil passage L3a extending linearly along the axial direction is formed inside the cylindrical protruding portion 16.
  • An end portion of the axial oil passage L3a on the second axial direction A2 side communicates with the radial oil passage L2c constituting the second oil passage L2 through the supply communication hole 71. That is, the axial oil passage L3a is formed so as to extend in the axial direction from a connecting portion with the second oil passage L2 (here, an end portion on the downstream side of the second oil passage L2).
  • a wall portion extending in the radial direction above the intermediate shaft M is formed with a radial oil passage L3b extending linearly along the radial direction.
  • the radial oil passage L3b has a radially inner end communicating with an end of the axial oil passage L3a on the first axial direction A1 side. Further, the radially outer end of the radial oil passage L3b is positioned further radially outward than the outer peripheral surface of the stator St, and the radial oil passage L3b communicates with the oil supply unit 50 at the position. Yes. That is, the radial oil passage L3b extends in the radial direction so as to communicate the axial oil passage L3a and the oil supply unit 50.
  • the pump cover 14 is formed with an axial cover communication hole 72 that extends in the axial direction and communicates with an opening formed on the surface in the first axial direction A1 side.
  • the cover communication hole 72 is formed radially outward from the outer peripheral surface of the stator St.
  • a partition through-hole 73 that penetrates the partition wall 12 in the axial direction is formed at a position overlapping the cover communication hole 72 in the partition wall 12 when viewed in the axial direction.
  • a cylindrical tubular member 51 extending linearly is inserted into the partition through hole 73 from the first axial direction A1 side.
  • the outer peripheral surface of the tubular member 51 is fitted to the inner peripheral surface of the partition through hole 73.
  • the end of the tubular member 51 on the first axial direction A1 side is sealed.
  • the tubular member 51 is fixed to the tube support member 53 provided on the first support wall 3 in a state where the end portion on the first axial direction A1 side is supported. In this way, the tubular member 51 supported by the partition through hole 73 and the tube support member 53 is disposed so as to extend linearly along the axial direction above the stator St. In this example, the tubular member 51 is disposed adjacent to the stator St on the radially outer side (upward) of the stator St.
  • the tubular member 51 is provided with a supply opening 52.
  • the supply opening 52 is provided so as to pass through the tubular member 51 in the radial direction of the tubular member 51 and open to the outer peripheral surface thereof.
  • two such supply openings 52 are provided at positions overlapping the coil end portion Ce in the radial direction view. That is, one of the two supply openings 52 is provided at a position overlapping with the first coil end portion Ce1 in the radial direction, and the other is provided at a position overlapping with the second coil end portion Ce2 in the radial direction. ing. Thereby, the two supply opening parts 52 are opened toward the coil end parts Ce1 and Ce2 above the coil end parts Ce1 and Ce2.
  • the oil discharged from the circulating hydraulic chamber H2 through the second oil passage L2 is the axial oil passage L3a, the radial oil passage L3b, the cover communication hole 72, the partition through hole 73, the inside of the tubular member 51 (inner peripheral surface). ) And the supply opening 52 to be supplied to the rotating electrical machine accommodation space S.
  • the oil introduced into the rotating electrical machine housing space S flows downward in the vertical direction and is supplied to the coil end portions Ce1 and Ce2 from the radially outer side.
  • the tubular member 51 is disposed above the stator St, and oil is supplied to the uppermost portion of the coil end portions Ce1 and Ce2 in the vertical direction.
  • the oil supply portion 50 that supplies oil to the coil end portions Ce1 and Ce2 from above the stator St is configured by the cover communication hole 72, the partition through hole 73, the tubular member 51, and the supply opening 52.
  • the axial oil passage L3a, the radial oil passage L3b, and the oil supply unit 50 constitute a part of the third oil passage L3 that supplies oil to the rotating electrical machine accommodation space S.
  • the coil end is formed from above the stator St via the axial oil passage L3a, the radial oil passage L3b, and the oil supply unit 50 that constitute the third oil passage L3.
  • Oil is supplied to the top of the part Ce.
  • the oil supplied to the uppermost part of the coil end part Ce is divided into both sides in the circumferential direction and flows down along the surface of the coil end part Ce in the vertical direction.
  • the heat of the coil end portion Ce is transmitted to the oil by heat exchange, thereby cooling the coil end portion Ce.
  • the whole of the stator St here, in particular, the coil end portion Ce
  • the coil end portion Ce can be efficiently cooled by oil supplied from above to the stator St.
  • the discharge oil passage L ⁇ b> 2 a constituting the second oil passage L ⁇ b> 2 is between the clutch hub 26 and the first radial extension portion 31 on the radially inner side than the fourth bearing 64. It has the gap oil passage mentioned above.
  • a third bearing 63 is disposed adjacent to the gap oil passage on the first axial direction A1 side.
  • the third bearing 63 is not perfect although it has a certain degree of liquid tightness, and a part of the oil from the gap oil passage is cylindrically projected from the third bearing 63, the input shaft I, and the first radially extending portion 31. Leak in the axial direction through the space between the portions 32.
  • the third oil passage L3 has a bearing supply oil passage L3c that branches from the gap oil passage, which is a connection portion with the second oil passage L2, and extends toward the first bearing 61.
  • the oil that has passed through the first bearing 61 while lubricating the first bearing 61 flows down between the first support wall 3 and the first radial extending portion 31 in the vertical direction, and the rotary electric machine housing space. S is supplied.
  • the third oil passage L3 has a bearing discharge oil passage L3d that supplies the oil discharged from the first bearing 61 to the rotating electrical machine housing space S.
  • a part of the third oil passage L3 is configured by the bearing supply oil passage L3c and the bearing discharge oil passage L3d.
  • the oil supplied to the rotating electrical machine accommodation space S through the bearing supply oil passage L3c and the bearing discharge oil passage L3d flows down downward in the vertical direction, or the rotor support member. Along with the rotation of 30, it is ejected radially outward. Thereby, oil is supplied to the first coil end portion Ce1 from the radially inner side.
  • the third oil passage L3 includes the bearing supply oil passage L3c and the bearing discharge oil passage L3d. The coil end portion Ce1) can be cooled.
  • the oil discharged from the circulation hydraulic chamber H2 through the second oil passage L2 is supplied to the third oil passage L3 (the oil passage through the tubular member 51 and the oil passage).
  • the coil end portion Ce of the stator St housed in the rotating electrical machine housing space S can be cooled by supplying to the rotating electrical machine housing space S via the first bearing 61 (including both oil passages passing through the first bearing 61). .
  • substantially the entire amount of oil passing through the second oil passage L2 is supplied to the rotating electrical machine accommodation space S through the third oil passage L3.
  • the oil for cooling the friction plate 27 and the oil for cooling the coil end portion Ce are almost completely shared, and the coil end portion Ce is cooled using the oil that has cooled the friction plate 27 as it is. be able to. Therefore, in the drive device D according to the present embodiment, it is possible to efficiently cool both the clutch CL and the rotating electrical machine MG while suppressing the amount of oil supplied from the oil pump 19 to be small.
  • Second Embodiment A second embodiment of the present invention will be described with reference to FIG. Also in this embodiment, the case where the vehicle drive device according to the present invention is applied to the drive device D for a hybrid vehicle will be described as an example.
  • the overall configuration of the drive device D according to this embodiment and the configuration of each part are basically the same as those of the first embodiment.
  • the first oil passage L3 which is a main component of the cooling structure of the rotating electrical machine MG, is formed below the intermediate shaft M (downward in the vertical direction). This is different from the embodiment.
  • differences from the first embodiment will be described. Note that points not particularly specified are the same as those in the first embodiment.
  • the intermediate shaft M is not formed with the radial oil passage L2c (see FIG. 3), and the downstream end of the axial oil passage L2b (in this example, the second axial direction A2 side).
  • the pump cover 14 is connected to the radially outer end of the radial oil passage L3f formed so as to extend radially inside the wall portion of the pump cover 14 below the intermediate shaft M.
  • the radial oil passage L3f extends linearly along the radial direction from the outer peripheral surface of the pump body 13 to the radially inner side.
  • the pump cover 14 is formed with an axial cover communication hole 76 that extends in the axial direction and communicates with an opening formed on the surface in the first axial direction A1 side.
  • a recess 77 that is recessed toward the first axial direction A1 side is formed at a position that overlaps the cover communication hole 76 when viewed in the axial direction on the side surface on the second axial direction A2 side of the pump body 13.
  • the recess 77 communicates with the third oil passage opening 17 that opens to the first axial direction A1 side, which is the rotating electrical machine MG side, through the throttle hole 78.
  • the radial oil passage L3f, the cover communication hole 76, the recess 77, the throttle hole 78, and the third oil passage opening 17 constitute a part of the third oil passage L3.
  • an oil passage that passes through the tubular member 51 (see FIG. 3) described in the first embodiment is not provided.
  • the third oil passage opening 17 is formed so as to open to a support contact surface 13a provided on the first axial direction A1 side of the pump body 13. That is, the third oil passage opening 17 is provided on the support contact surface 13 a that is a contact surface with the sensor stator 23 in the pump body 13.
  • a supply through hole 23 a penetrating the sensor stator 23 in the axial direction is provided at a position overlapping the third oil passage opening 17 in the axial direction of the sensor stator 23.
  • the supply through hole 23a corresponds to an “axial through hole” in the present invention.
  • the inner diameter of the third oil passage opening 17 is set larger than the inner diameter of the throttle hole 78, and the inner diameter of the supply through hole 23 a is set larger than the inner diameter of the third oil passage opening 17. Yes.
  • an oil collecting portion 56 is provided on the radially outer side of the third oil passage opening 17.
  • the oil collecting portion 56 is formed in the second radially extending portion 36 of the rotor support member 30 so as to open radially inward.
  • the oil collecting portion 56 is disposed between the second radially extending portion 36 formed in a flat plate shape and the sensor rotor 22 disposed in parallel to the second radially extending portion 36. Is formed.
  • a step portion is formed on the inner peripheral portion of the cylindrical sensor mounting portion 38 as a whole, and a portion on the second axial direction A2 side with respect to a portion on the first axial direction A1 side of the step portion.
  • it is formed so as to have a large diameter with respect to its inner diameter. That is, the sensor attachment portion 38 has an attachment large diameter portion 38a and an attachment small diameter portion 38b that are formed to be aligned in the axial direction.
  • the sensor rotor 22 has a side surface on the first axial direction A1 side in contact with a side surface (that is, a step surface) on the second axial direction A2 side of the small mounting diameter portion 38b, and a radially outer end portion on the large mounting portion.
  • An oil collecting portion 56 is formed as an annular space having a rectangular cross section formed between the side surface on the direction A1 side. The oil collecting part 56 can efficiently collect and store the oil supplied through the third oil passage opening 17 and the supply through hole 23a.
  • the drive device D includes a fourth oil passage L ⁇ b> 4 for supplying the oil collected by the oil collecting unit 56 to the rotating electrical machine accommodation space S. Therefore, in the present embodiment, the third oil passage L3 supplies the oil discharged from the circulation hydraulic chamber H2 through the second oil passage L2 to the rotating electrical machine accommodation space S through the fourth oil passage L4.
  • a fourth oil passage L4 is formed at least in the rotor support member 30, and is formed so as to open inward in the radial direction of each of the coil end portions Ce1 and Ce2.
  • the fourth oil passage L4 includes a common oil passage L4a and a radial oil passage L4b that extend radially inside the rotor support member 30, and an axial oil passage L4c that extends inside the rotor support member 30 in the axial direction. Yes.
  • the common oil passage L4a is formed so as to extend linearly from the oil collecting portion 56 to the sensor attachment portion 38 (here, the attachment small diameter portion 38b) in the second radial extension portion 36 along the radial direction.
  • a plurality (for example, eight) of common oil passages L4a are arranged evenly distributed in the circumferential direction.
  • the common oil passage L4a is formed so that the radially inner portion of the second support portion 43 in the axially extending portion 41 also extends linearly along the radial direction.
  • the radial oil passage L4b communicates with the rotating electrical machine housing space S by extending a radially outer portion of the second support portion 43 linearly along the radial direction from the radially outer end of the common oil passage L4a. ing.
  • the axial oil passage L4c communicates with the rotating electrical machine housing space S by extending the second support portion 43 and the rotor Ro linearly along the axial direction from the radially outer end of the common oil passage L4a.
  • the axial oil passage L4c includes a portion extending in the axial direction inside the second support portion 43, a portion formed between the outer peripheral surface of the axial extension portion 41 and the groove portion of the rotor Ro, and the rotor.
  • a radial through hole 44 a provided in the holding member 44.
  • a plurality (for example, four) of radial oil passages L4b and a plurality of (for example, four) axial oil passages L4c are alternately arranged in the circumferential direction.
  • the oil collecting portion 56 communicates with the rotating electrical machine housing space S through the fourth oil passage L4.
  • the axial oil passage L4c branched from the common oil passage L4a and extending in the axial direction is formed so as to open to the inside in the radial direction of the first coil end portion Ce1.
  • the opening on the rotating electrical machine accommodation space S side of this axial oil passage L4c (the opening on the radially outer side of the through hole 44a of the rotor holding member 44) is located at a position overlapping the first coil end portion Ce1 in the radial direction. Is formed.
  • the radial oil passage L4b branched from the common oil passage L4a and extending in the radial direction is formed so as to open inward in the radial direction of the second coil end portion Ce2.
  • the opening on the rotating electrical machine accommodation space S side of the radial oil passage L4b is formed at a position overlapping the second coil end portion Ce2 in the radial direction.
  • Such a fourth oil passage L4 supplies oil from the oil collecting portion 56 to the coil end portions Ce1 and Ce2.
  • the coil end portions Ce1 and Ce2 are cooled as follows. First, the oil discharged from the circulation hydraulic chamber H2 through the second oil passage L2 is supplied to the radial oil passage L3f, the cover communication hole 76, the concave portion 77, the throttle hole 78, the third oil passage opening 17, and the supply penetration. It is supplied to the space inside the first case through the hole 23a. Thereafter, the oil is collected by the oil collecting portion 56 and supplied to the coil end portions Ce1 and Ce2 of the stator St housed in the rotating electrical machine housing space S through the fourth oil passage L4.
  • the oil collecting unit 56 is configured by using the sensor rotor 22 of the rotation sensor 21.
  • a rotation sensor 21 is provided in the driving device D including the rotating electrical machine MG as a driving force source of the vehicle as in the present embodiment.
  • the oil collection part 56 is formed without requiring an additional member, and cost reduction and the miniaturization of the drive device D are achieved.
  • the radial oil passage L2c constituting the second oil passage L2 is the end portion on the axial second direction A2 side of the axial oil passage L3a constituting the third oil passage L3.
  • the case where it communicates with was described as an example.
  • the embodiment of the present invention is not limited to this. That is, for example, a configuration in which the radial oil passage L2c communicates with an arbitrary portion other than the end portion on the axial second direction A2 side in the axial oil passage L3a is also a preferred embodiment of the present invention.
  • a configuration in which the radial oil passage L2c communicates with an arbitrary portion other than the end portion on the axial second direction A2 side in the axial oil passage L3a is also a preferred embodiment of the present invention.
  • the third oil passage L3 does not include the axial oil passage L3a, and the radial oil passage L2c communicates with the radially inner end of the radial oil passage L3b constituting the third oil passage L3. It is one of the preferred embodiments of the present invention to have a configuration.
  • the embodiment of the present invention is not limited to this. That is, it is preferable that the oil from the supply opening 52 is configured to be supplied to at least the upper portion of the coil end portion Ce, for example, a region within a predetermined range in the circumferential direction including the uppermost portion of the coil end portion Ce. It is also one of the preferred embodiments of the present invention that the oil is supplied from the supply opening 52 to the tank.
  • the oil supply unit 50 includes the tubular member 51 having the supply opening 52
  • the embodiment of the present invention is not limited to this. That is, it is possible to configure the oil supply unit 50 without including such a tubular member 51.
  • the oil supplied to the rotating electrical machine accommodation space S through the cover communication hole 72 and the partition through hole 73 is jetted in the axial direction and reaches one or both of the coil end portions Ce1 and Ce2.
  • the inner diameters of the cover communication hole 72 and the partition through hole 73 are preferably reduced so that the oil appropriately reaches the first coil end portion Ce1.
  • a hook-like member capable of collecting oil supplied through the cover communication hole 72 and the partition through-hole 73 is installed on the upper portion of the stator St, and at a predetermined position of the hook-like member. It is also one of preferred embodiments of the present invention that a supply opening 52 is provided and oil is supplied from the supply opening 52 to the coil end portions Ce1 and Ce2. Alternatively, an oil passage extending in the axial direction is formed in the case peripheral wall 2, and a supply opening 52 is provided at a predetermined position on the inner peripheral surface of the case peripheral wall 2, and oil is supplied from the supply opening 52 to the coil end portions Ce 1 and Ce 2. It is also one of the preferred embodiments of the present invention to be configured to supply.
  • the case where the third oil passage opening 17 is provided on the support contact surface 13a of the pump body 13 has been described as an example.
  • the embodiment of the present invention is not limited to this. That is, a configuration in which the third oil passage opening 17 is provided in a portion other than the support contact surface 13a in the pump body 13 is also a preferred embodiment of the present invention.
  • a configuration in which the third oil passage opening 17 is provided on the side surface or the outer peripheral surface of the cylindrical protrusion 15 on the first axial direction A1 side can be employed.
  • a configuration in which the third oil passage opening 17 is provided in a portion other than the pump body 13 in the second support wall 11 is also one preferred embodiment of the present invention.
  • the third oil passage opening 17 is provided on the side surface of the partition wall 12 on the first axial direction A1 side.
  • the sensor stator 23 may not be provided with the supply through hole 23a.
  • the number of the oil collecting portions 56 can be arbitrary (however, even numbers are preferable), and accordingly, the fourth oil passage L4 (the common oil passage L4a, the radial oil passage L4b, and the axial oil passage). L4c) is determined.
  • the embodiment of the present invention is not limited to this. That is, for example, a plate-like thin plate member may be used in place of the sensor rotor 22, and the oil collecting portion 56 may be formed between the second radially extending portion 36 and the thin plate member.
  • the rotation sensor 21 can be disposed at an arbitrary position.
  • the rotation sensor 21 is located between the first support wall 3 and the first radially extending portion 31 on the axial first direction A1 side with respect to the rotor support member 30. It is possible to adopt a configuration in which the rotation sensor 21 is arranged.
  • the fourth oil passage L4 has both the radial oil passage L4b and the axial oil passage L4c, and the first coil end portion Ce1 and the second coil end portion Ce2.
  • the case where it was formed so that it may open in the radial direction inner side of both was demonstrated as an example.
  • the embodiment of the present invention is not limited to this. That is, for example, the fourth oil passage L4 has only one of the radial oil passage L4b and the axial oil passage L4c, and one of the first coil end portion Ce1 and the second coil end portion Ce2. It is also one of preferred embodiments of the present invention to have a structure formed so as to open only inward in the radial direction.
  • the case where the drive device D is provided with only the oil path which passes along the tubular member 51 and the 1st bearing 61 as the 3rd oil path L3 is an example.
  • the drive device D includes only the oil passage that passes through the third oil passage opening 17 and the oil passage that passes through the first bearing 61 as the third oil passage L3.
  • the case has been described as an example.
  • the embodiment of the present invention is not limited to this. That is, the drive device D includes the oil passage that passes through the tubular member 51, the oil passage that passes through the third oil passage opening 17, and the oil passage that passes through the first bearing 61 as the third oil passage L3.
  • the configuration is also one of the preferred embodiments of the present invention.
  • the driving device D includes any one of these three oil passages or a combination of any two as the third oil passage L3. It is.
  • the third oil passage L3 for supplying the oil discharged from the circulation hydraulic chamber H2 through the second oil passage L2 to the rotating electrical machine housing space S it may be configured to further include an oil passage other than these. It is one of the preferred embodiments of the present invention.
  • the driving device D has a multi-axis configuration suitable for mounting on an FF (Front Engine Front Drive) vehicle.
  • the embodiment of the present invention is not limited to this.
  • the output shaft of the speed change mechanism TM is arranged on the same axis as the input shaft I and the intermediate shaft M, and is directly connected to the output differential gear device DF.
  • the drive device D having such a configuration is suitable when mounted on an FR (Front Engine Rear Drive) vehicle.
  • the present invention includes an input member that is drivingly connected to an internal combustion engine, an output member that is drivingly connected to a wheel, a friction engagement device that selectively drives and connects the input member and the output member, an input member, and an output member. And a rotating electric machine provided on a power transmission path connecting the two.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • General Engineering & Computer Science (AREA)
  • Hybrid Electric Vehicles (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)
  • Motor Or Generator Cooling System (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne un dispositif d'entraînement pour un véhicule, configuré de manière à pouvoir refroidir efficacement à la fois un organe de friction et une machine dynamoélectrique tout en réduisant la quantité d'huile alimentée à l'organe de friction. Le dispositif d'entraînement (D) pour véhicule comprend : un organe d'entrée (I) relié pour transmettre une force motrice au moteur à combustion interne (E) ; un organe de sortie relié pour transmettre une force motrice aux roues ; un dispositif d'engagement à friction (CL) servant à relier de manière sélective l'organe d'entrée (I) et l'organe de sortie pour transmettre une force motrice ; et une machine dynamoélectrique (MG) installée sur la voie de transmission motrice qui relie l'organe d'entrée (I) et l'organe de sortie. Le dispositif d'entraînement (D) pour un véhicule comprend également : une chambre contenant de l'huile (H2) servant au moins à contenir les organes de friction (27) du dispositif d'engagement à friction (CL) et remplie d'huile ; un espace conteneur (S) pour contenir la machine dynamoélectrique (MG) ; un premier circuit d'huile (L1) pour fournir l'huile à la chambre contenant l'huile (H2) ; un deuxième circuit d'huile (L2) pour refouler l'huile de la chambre contenant l'huile (H2) ; et un troisième circuit d'huile (L3) pour fournir l'huile refoulée depuis le circuit d'huile (L2) dans l'espace conteneur (S).
PCT/JP2011/071333 2010-09-24 2011-09-20 Dispositif d'entraînement pour véhicule WO2012039378A1 (fr)

Priority Applications (2)

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CN201180041612XA CN103081311A (zh) 2010-09-24 2011-09-20 车辆用驱动装置
DE112011102544T DE112011102544T5 (de) 2010-09-24 2011-09-20 Fahrzeugantriebsvorrichtung

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JP2010-213447 2010-09-24
JP2010213447 2010-09-24
JP2011-043269 2011-02-28
JP2011043269A JP2012086826A (ja) 2010-09-24 2011-02-28 車両用駆動装置

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WO2012039378A1 true WO2012039378A1 (fr) 2012-03-29

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JP (1) JP2012086826A (fr)
CN (1) CN103081311A (fr)
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WO (1) WO2012039378A1 (fr)

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WO2013118901A1 (fr) * 2012-02-10 2013-08-15 アイシン・エィ・ダブリュ株式会社 Dispositif d'entraînement hybride
WO2014051110A1 (fr) * 2012-09-28 2014-04-03 アイシン・エィ・ダブリュ株式会社 Dispositif d'entraînement hybride
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CN107738570A (zh) * 2017-10-25 2018-02-27 哈尔滨东安汽车发动机制造有限公司 一种用于混合动力车的耦合机构
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WO2019208081A1 (fr) * 2018-04-27 2019-10-31 日本電産株式会社 Unité de moteur et dispositif d'entraînement de véhicule
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DE102019111832A1 (de) * 2019-05-07 2020-11-12 Schaeffler Technologies AG & Co. KG Hybridmodul sowie Antriebsanordnung für ein Kraftfahrzeug
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DE112011102544T5 (de) 2013-05-02
CN103081311A (zh) 2013-05-01
JP2012086826A (ja) 2012-05-10
US20120080286A1 (en) 2012-04-05

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